EP1026300B1 - Schmiereinrichtung für mehrere Schmierstellen - Google Patents

Schmiereinrichtung für mehrere Schmierstellen Download PDF

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Publication number
EP1026300B1
EP1026300B1 EP00100024A EP00100024A EP1026300B1 EP 1026300 B1 EP1026300 B1 EP 1026300B1 EP 00100024 A EP00100024 A EP 00100024A EP 00100024 A EP00100024 A EP 00100024A EP 1026300 B1 EP1026300 B1 EP 1026300B1
Authority
EP
European Patent Office
Prior art keywords
piston
lubrication
rotation
lubrication device
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00100024A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1026300A2 (de
EP1026300A3 (de
Inventor
Rolf Huss
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Memminger IRO GmbH
Original Assignee
Memminger IRO GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Memminger IRO GmbH filed Critical Memminger IRO GmbH
Publication of EP1026300A2 publication Critical patent/EP1026300A2/de
Publication of EP1026300A3 publication Critical patent/EP1026300A3/de
Application granted granted Critical
Publication of EP1026300B1 publication Critical patent/EP1026300B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N13/00—Lubricating-pumps
    • D—TEXTILES; PAPER
    • D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
    • D04B—KNITTING
    • D04B35/00—Details of, or auxiliary devices incorporated in, knitting machines, not otherwise provided for
    • D04B35/28—Devices for lubricating machine parts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/15—Intermittent grip type mechanical movement
    • Y10T74/1526—Oscillation or reciprocation to intermittent unidirectional motion
    • Y10T74/1527—Screw and nut devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19623—Backlash take-up

Definitions

  • the invention relates to a lubricating device for several lubrication points, especially for lubricant supply from smudges of a knitting machine, preferably with oil, according to the preamble of patent claim 1.
  • a lubricating device known to be a reliable and metered Lubrication of several lubrication points allowed.
  • the Lubricating device has a lubricant container, in which a piston pump is housed.
  • the output of the Piston pump is connected to a motor-driven distribution valve, around the output of the pump with one each To connect lubricant line, which consists of a group of Lubricant lines is selected.
  • the pump cylinder has multiple outgoing lubrication lines. By an axial movement of the piston is displaced oil thus directed to the lubrication lines.
  • An engine control unit is intended to time the oscillating armature drive Time to excite.
  • JP-A-179799 a lubricating device known that a pump cylinder with several radial having outgoing lubrication lines.
  • a piston is both axially displaceable and rotatable stored.
  • the piston has a control channel to the pump volume with one of its rotational position corresponding connecting outgoing oil channel.
  • a drive device is intended to control the piston both turn to activate the outgoing lines one after the other, as well as the piston to move axially to the Effecting pumps.
  • the drive device includes a at its periphery with a wavy groove provided cylinder, the axial firmly connected to the piston.
  • the piston faces the cylinder, however, a great rotational play.
  • a spring element biases the piston in the direction of rotation when the Cylinder is rotated.
  • stop screws are assigned. The radial arm abuts the cylindrical surface of these screws at. At the top and bottom, however, he can pass by.
  • This drive device forces the lubrication of Lubrication points in specified order:
  • One variable Lubrication of the individual lubrication points is not possible.
  • the lubrication device in the lubrication device according to the invention is a Distributor provided with the by a pump supplied lubricant branches on selected lines and thus be supplied to selected lubrication points can.
  • the distributor device and the pumping device are combined into one unit. By summarizing of distribution device and pumping device to a unit simplifies the construction of the lubrication device considerably. In addition, the control of the Lubrication be simplified.
  • the pumping device is designed as a piston pump and has a piston axially displaceable in a cylinder on. This serves together with the cylinder as a pump organ.
  • the cylinder and the piston as a control element educated. For this he is rotatable in the cylinder stored and provided with control surfaces or channels, which in the cylinder arranged control slots or outlets assigned.
  • the piston can on its lateral surface be provided with at least one control channel, the so is formed that he by appropriate rotational positioning the piston respectively in accordance with at least one of the outlet channels can be brought. If necessary, the arrangement can also be made so that the control channel with several outlet channels in accordance transferred is.
  • control channel and the outlet channels are In doing so, arranged so that of the piston in the cylinder defined working space over the entire stroke of the piston with the selected outlet channel in combination stands. In this way, the whole, from the piston displaced oil volumes are conveyed into the outlet channel.
  • the piston pump designed in this way is at the same time pumping device and distribution device.
  • the pumping device and the distributor device is connected to a drive device, which is the Turning and moving the piston causes.
  • the Displacement movement is a pumping movement, so that the Displacement drive forms a pump drive.
  • the rotational movement of the piston has, if no displacement movement, no volume change in the cylinder result, whereby of the rotational movement only the blocking or release controlled by exhaust ducts.
  • the rotary drive is thus a distributor drive and the piston is so far a Spool.
  • To rotate the piston is preferably a stepper motor used, which is a desired rotary actuator movement generated.
  • a stepper motor used, which is a desired rotary actuator movement generated.
  • To be made rotary positions to choose from an outlet channel and thus to activate a Lubrication points are easy to carry out with a stepper motor. From this stepping motor, however, can also Displacement movement of the piston are derived. Is to this via a coupling with the stepper motor or other servomotor connected to the first one set or adjustable rotation allows, where the relative rotation within the rotational play with a gear means converted into the desired linear motion becomes.
  • the angle of rotation of the rotary game can be used to generate a Linear motion can be exploited.
  • This is the piston connected to a locking device that the Pistons in any or selected rotational positions holds without rotation, without its axial displacement too To block.
  • this locking device by a Locking wheel be formed with a locking member in and can be disengaged. This is preferably done by suitable radial movement of the locking member, eg. by means of a pull magnet.
  • the coupling device possible.
  • the displacement device now formed by a gear that this relative rotation between the piston and the rotating device converted into a linear movement of the piston.
  • the lock-wheel is designed as a ratchet wheel.
  • the blocking element then acts as a locking pawl, the a rotation of the locking wheels in a selected direction allows.
  • the locking pawl for example.
  • a solenoid be releasable to the other direction of rotation of the lock-wheel.
  • the transmission can be engaged by two with each other be present threaded elements formed.
  • the slope of the Thread of the threaded elements is dimensioned so that by the relative rotation between piston and actuator in Framework of the rotational play of the coupling device a complete Piston stroke is passed through.
  • By forward or Backward rotation of the servo motor is the piston or movable.
  • Such a cam mechanism can by a provided in the wall of a socket wavy annular groove be formed in the one of the Servomotor driven, extending in the radial direction Pen or finger is running.
  • the linear motion generating gear is preferably biased. This can, for example, by means of a Magnets happen, the sliding flanks of the Gearbox holds in plant. This is especially true on the correct dosage of the lubricant of advantage. If the drive reverses its direction of rotation, e.g. of a To change the piston stroke to a piston return stroke are the Turnaround points are precisely defined and incorrect dosages become avoided.
  • the leading out of the cylinder outlet channels and an inlet channel are preferably each with check valves Mistake.
  • the pumping device is thus without further control means.
  • the check valves are preferably automatic, from the applied differential pressure, controlled valves. Other valve control devices are not mandatory.
  • a sensor device advantageous be that detects and monitors the stroke of the piston. It may be sufficient to monitor whether the piston reached a certain stroke or not. Is, for example, a Lubricating duct clogged, the piston can not lubricate Pump into this channel and blocked. He then reaches the Switching point of the sensor device does not detect this and the corresponding machine shuts off.
  • any distribution devices and connected Lines and the number of connected lubrication points it is appropriate to the pump pressure during individual To modulate lubrication pulses.
  • the pauses between individual micropump pulses are suitably dimensioned such that the pressure in the lines does not reach a minimum limit below.
  • the minimum pressure is preferably something less than the required injection pressure of the connected Nozzles. He is sufficient, any compliances (elasticities) the cables under bias. Thereby It is possible, especially small amounts of lubricant dosing or to extend the lubrication process in time.
  • FIG. 1 illustrates a lubricating device 1, to which a reservoir 2 for lubricants, For example, oil, heard.
  • a distribution and pumping unit 3 is used, which is connected to a Group 4 leading lubricant lines 5a to 51 to predetermined times predetermined lubricant portions emits.
  • FIG. 1 pump and Distribution unit 3 For conveying and allocating the lubricant serves a piston pump 7, the same time pumping device 7a and distributor 7b. Belongs to the piston pump 7 as is apparent in particular from FIGS. 3 and 7, a cylinder body 8 with a cylindrical through hole 9.
  • the through hole 8 is at one, in Figures 2 and 7 lower end formed as a stepped bore, by enlarging a section 10 Diameter. This serves to accommodate a Check valve 12, the valve body 14, for example, in a screwed corresponding thread of section 10 is.
  • the valve body 14 is provided with a passage 15 provided for receiving a valve closure member 16.
  • a valve closure member 16 Of the Head of the valve closure member 16 has to that of the Through hole 9 specified interior of the cylinder body 8. If necessary, a not further illustrated Spring the valve closure member against a Clamp on the valve body 14 formed valve seat.
  • the valve body 8 is a plurality, in the present Example twelve radial bores 17 (17a to 17l; FIG. 3) provided, which are arranged in a common plane 18 are on which the through hole 9 is vertical.
  • the Radial bore 17a to 171 are at equal angular intervals arranged to each other while the distance between the Radial bore 171 and the radial bore 17a slightly larger is considered the otherwise uniform distances between the Radial holes 17a to 171.
  • radial bores 17th Reference without letter index refers to all radial bores 17a to 171 alike
  • check valves used a Fluid flow in the radial outward direction, i. from the Through hole 9 through the of the respective radial bore 17 formed outlet channel to the outside, but not allow back.
  • lubricant lines 5a to 51 connected, leading to the lubrication points.
  • the check valves may, if necessary, at a the distributor 7b remote end of the respective Line 5a to 51 are provided, in which case in the radial bores 17 only connecting nipple are screwed in.
  • a piston 21 is inserted, the outer diameter substantially with the Inner diameter of the through hole 9 matches, so Although the piston is axially displaceable and rotatable in the Through hole 9 is seated, but relatively tight with this a working space 22 limited ( Figure 2).
  • the piston 21st has in addition to its cylindrical lateral surface 23 a largely planar end face 24. Starting from the End face 24 extends a cam 25 in parallel to its central axis 26 over the lateral surface. The length the cam 25 is preferably the same size or slightly larger than the level 18 distance of one "upper" piston dead center 27, which in Figure 2 by a dashed Line is indicated.
  • the piston 21 reaches the top dead center 27 with its end face 24 when the Working space 22 smallest, i. the piston 21 in Figure 2 is in its lowest position.
  • the control groove 25 is, as Figure 3 illustrates, formed relatively narrow and extends in the circumferential direction on the lateral surface 23 over a peripheral region, the approximately with the diameter of the radial bores 17 at the Wall of the through hole 9 matches.
  • the depth the control groove 25 is dimensioned such that the flow resistance in the control groove 25 is not essential is greater than in the radial bores 17th
  • the piston 21 is at its out of the cylinder piece. 8 out projecting end in a connection sleeve 29 taken and pinned with it (pin 30).
  • the Connecting sleeve 29 via a further pin 31 with a Actuating rod 32 connected to a drive device 33 leads.
  • the actuating rod 32 is rotationally fixed and fixed in the axial direction with a coupling half 34th connected, the two extending in the axial direction as well as parallel and spaced apart webs 35, 36. Between these are windows 37, 38 formed, which can be seen in particular from Figure 6 are.
  • the coupling half 34 belongs to a coupling device 39, the other coupling half 40 of one of a shaft 41 driven radial pin 42 is formed. This engages with its two ends in the window 37, 38 and can each after going through a certain, here fixed at 90 °, with one flank each the webs 35, 36 come into contact.
  • the shaft 41 also carries a apparent from Figure 7 Socket 43, which connects to the radial pin 42 and the one on its outside Threaded element 44 is provided.
  • This has a multi-course External thread on. His gradient is such that over 90 ° of the circumference of the threaded member 44 in the axial direction a path is taken that is complete Piston stroke of the piston 21 corresponds.
  • the threaded element 44 is in operation with a Threaded element 45 in conjunction, which can be seen in FIG and in an annular, from the webs 35, 36 of the Coupling half 34 carried element or section is trained. This changes the coupling half 34th when passing through the rotational clearance of the clutch 39 its axial position opposite the coupling half 40th
  • Section of the coupling half 34 is on its outside designed as a lock-wheel 46. This points in the axial direction extending, in cross-section approximately trapezoidal, Teeth 47, which serve to the coupling half 34th rotatably, but axially displaceable to lock. This is removed from Figure 4.
  • a locking latch 48 Radial to the lock-wheel 46 is a locking latch 48 slidably mounted.
  • the locking bar 48 is by a compression spring 49 on its radial biased outward position, in which he does not with the Locking wheel 46 is engaged.
  • a solenoid 51 is used to, with its anchor 52 via a corresponding rod 53 the lock-latch 48 in engagement with the lock-wheel 46 to bring, so that its rotation in predetermined by the teeth 47 discrete positions is blocked.
  • These Blocking or blocking positions respectively correspond to rotational positions, in which the control groove 25 ( Figure 3) with a the radial bores 17 is aligned. Accordingly, thirteen Interdental spaces present, twelve of which Positions of the radial bores 17 and the thirteenth, the larger space between the radial bores 171 and 17a correspond. The size of the interdental spaces corresponds the size of the distances of the radial bores 17th
  • the coupling half 40 is rotationally fixed to the shaft 41 connected to the output shaft of a stepping motor 55 forms. This is coaxial with the actuating rod 32nd aligned and supported by a corresponding holder 56.
  • the multi-part holder 56 also carries the lifting magnet 51 and has a tubular, itself tapered, coaxial with the actuating rod 32 arranged Extension 57 on, at its lower free End carries the pump unit 7. He has a flange here Extension 58, on which the lubricant lines 5 can be held and also a microsieve 59th wearing. This is pot-shaped and encloses the lower end of the extension 57.
  • the intake valve 12 incoming lubricant the microsieve 59th happen with what he is filtered.
  • the coupling half 34 is at its the actuating rod 32 facing side provided with a hub 60, which has an external thread 61.
  • a hub 60 On the hub 60 is a in Figure 7 separately shown annular axial polarized permanent magnet 62 held by a nut 63, for which the external thread 61 is provided.
  • the Permanent magnet 62 generates by means of its magnetic field Force, the threaded element 44 with the thread 45 backlash engaged. This serves to reverse the direction of rotation the stepping motor 55 an undesirable backlash in the gearbox to avoid that from the threaded element 44 and the internal thread 45 is formed and for implementation a rotational movement in a linear movement is used.
  • the actuating rod 32 is on the extension 57 in a sleeve 65 which supports the connecting sleeve 29 adjacent in a corresponding intermediate wall of the extension 57 is arranged.
  • the socket 65 leaves a rotary and an axial movement of the actuating rod 32 to.
  • a magnetic sensor for example, a Hall sensor 66, which determines the position of the permanent magnet 62 recorded and at least the exceeding or falling below a Switching position different. If necessary, a another Hall sensor or another position sensor 67 may be provided in the vicinity of the transverse pin 42 to to record its position. Both the Hall sensors 66, 67 and the stepping motor 55 and the solenoid 51 are connected to a control device which the Lubricating device 1 controls as follows:
  • the locking wheel 46 is held against rotation.
  • the transverse pin 42 starts at the webs 35, 36, stops the stepper motor 55. It is now the pull magnet 51 de-energized, whereby the lock-wheel 46 is released.
  • the Stepping motor 55 which has served to here, the Piston 21 to give a lifting movement, now positioned the now freely rotatable locking wheel 46 by one tooth on.
  • the transverse pin 42 takes the webs 35, 36 and thus the coupling half 34 with.
  • the control groove 25 is characterized in accordance with the radial bore 17 a transferred.
  • the lubricant line 5a is now the stepper motor 55 in Counterclockwise controlled. Due to the size of the Window 37, 38 is the rotary motion here on a quarter Rotation limited. The stepper motor 55 passes through this Way, this rotational movement is due to interaction of the Threaded element 44 with the internal thread 45 in an in Figure 2 downward axial movement of the coupling half 34 implemented. About the actuating rod 32nd the piston 21 without turning down in Direction moved to its top dead center 27 out. Corresponding is the displaced oil on the lubricant line 5a delivered. It does not have to be the whole, for Available way to be gone through. The stepper motor 55 can be stopped before spending a quarter Has undergone rotation. Accordingly, then becomes a smaller Oil delivered. This is a fine dosage the dispensed oil portions possible.
  • stepper motor 55 is again operated clockwise until the transverse pin 42 again starts at the webs 35, 36. It Now, the tension 51 is released, causing the compression spring 49 moves the locking bar 48 radially outward and the lock-wheel 46 releases.
  • the stepper motor can now under Entrainment of the coupling half 34 and thus under rotation of the piston 21 by one tooth (if necessary, by several Teeth) continue to drive to the next lubrication position.
  • the rudder groove 25 is now in agreement brought with the radial bore 17b.
  • This is repeated in connection with the radial bore 17a described game again. As described so sequentially controlled all radial bores 17 and thus all lubricant lines 5 separately with suitable Oil portions are supplied.
  • the delivery of an oil portion can, as illustrated in FIG. 8, take place in pulses, the injection pressure p established by the pump device 7a being modulated within a lubrication interval t 1 , t 2 .
  • the stepper motor 55 is controlled step by step and moved, so that the piston 21 is also moved stepwise.
  • the pressure p can each drop slightly below a pressure limit p 1 .
  • the connected nozzles start to spray. If the pressure in the meantime drops below this value, eg to a slightly lower value p 0 , the nozzles will jet intermittently.
  • the inflow v ⁇ 1 to the nozzles thereby fluctuates and due to the elasticity of the lines in time.
  • the nozzles deliver the oil flow v ⁇ 2 drop by drop as micro-pulses, so that the oil flow is zero due to the short-term pressure drops between individual drops. In this way, even small amounts of oil can be released in time with relatively large, non-blockage-prone nozzles in the spray jet.
  • the piston 21 When starting the lubrication device 1 can first a venting of the pumping device 7a required become.
  • the piston 21 is in a venting position turned, in which his control groove 25 with a Radial bore 171 matches, which is open to the outside and in which no check valve is arranged.
  • One or several complete piston strokes now cause expulsion of air and filling the pumping volume with oil. Then the proper operation can be started.
  • FIG. 1 A modified embodiment of the locking mechanism is illustrated in FIG.
  • the lock wheel 46 is here designed as a ratchet wheel.
  • the locking bar 48 is as Pawl trained. It is therefore unnecessary, the Pull magnet for each indexing of the lock-wheel 46th head for.
  • the locking bar 48 is on the lock-wheel 46th spring-loaded. It allows rotation of the Ratchet wheel 46 in the clockwise direction (arrow 70) for Rotation of the piston 21 and thus for actuation of the distributor. In the opposite direction (arrow 71), however, each Rotation locked so that the pumping action is performed can be. An actuation of the solenoid 51 is only still required in very few exceptional cases.
  • FIG. 10 A further modified embodiment is shown in FIG. 10 illustrates.
  • the teeth of the lock-wheel 46 has Teeth 47 with a relatively low edge slope.
  • the locking bar 48 is resilient than in the radial direction Latch formed.
  • the control of the rotational movement of the Piston 21 takes place in this embodiment by the Stepper motor 55 when the game of the coupling device 39 is passed, the cogging torque of the locking bolt right or counter-clockwise overcomes.
  • a pumping device 7a For a lubrication device for several lubrication points, in particular for the supply of lubricant Knitting machines, a pumping device 7a is provided, which also serves as a distributor device 7b. For this purpose points the pumping device 7 a piston 21, which with a Control groove 25 is provided. The corresponding pump cylinder has one inlet and several on the cylinder wall distributed outlets on. Depending on which of the outlets the cam groove 25 of the piston 21 in accordance is brought, a corresponding lubrication point is selected. The pumping device 7 is thus at the same time Distribution facility.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Knitting Machines (AREA)
  • Transmission Devices (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Lubricants (AREA)
  • Auxiliary Weaving Apparatuses, Weavers' Tools, And Shuttles (AREA)
  • Mounting, Exchange, And Manufacturing Of Dies (AREA)
  • Looms (AREA)
  • Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
  • Materials For Medical Uses (AREA)
  • Measurement And Recording Of Electrical Phenomena And Electrical Characteristics Of The Living Body (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Professional, Industrial, Or Sporting Protective Garments (AREA)
  • General Details Of Gearings (AREA)
  • Steroid Compounds (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Braking Arrangements (AREA)
EP00100024A 1999-02-05 2000-01-04 Schmiereinrichtung für mehrere Schmierstellen Expired - Lifetime EP1026300B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19904647A DE19904647A1 (de) 1999-02-05 1999-02-05 Schmiereinrichtung für mehrere Schmierstellen
DE19904647 1999-02-05

Publications (3)

Publication Number Publication Date
EP1026300A2 EP1026300A2 (de) 2000-08-09
EP1026300A3 EP1026300A3 (de) 2001-04-11
EP1026300B1 true EP1026300B1 (de) 2005-12-28

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EP00100024A Expired - Lifetime EP1026300B1 (de) 1999-02-05 2000-01-04 Schmiereinrichtung für mehrere Schmierstellen

Country Status (22)

Country Link
US (2) US6322336B1 (sk)
EP (1) EP1026300B1 (sk)
JP (1) JP3842000B2 (sk)
KR (1) KR100371978B1 (sk)
CN (1) CN1188597C (sk)
AT (1) ATE314513T1 (sk)
BR (1) BR0000306A (sk)
CA (1) CA2298296C (sk)
CO (1) CO5231265A1 (sk)
CZ (1) CZ294191B6 (sk)
DE (2) DE19904647A1 (sk)
ES (1) ES2255900T3 (sk)
HK (1) HK1030040A1 (sk)
ID (1) ID24778A (sk)
MY (1) MY123504A (sk)
PE (1) PE20010158A1 (sk)
PL (1) PL338066A1 (sk)
RU (1) RU2185566C2 (sk)
SK (1) SK284957B6 (sk)
TR (1) TR200000298A3 (sk)
TW (1) TW473603B (sk)
UA (1) UA59404C2 (sk)

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US9140407B2 (en) * 2010-11-29 2015-09-22 Lincoln Industrial Corporation Pump having stirrer and direct feed
US9222618B2 (en) 2010-11-29 2015-12-29 Lincoln Industrial Corporation Stepper motor driving a lubrication pump providing uninterrupted lubricant flow
US9388940B2 (en) 2010-11-29 2016-07-12 Lincoln Industrial Corporation Variable speed stepper motor driving a lubrication pump system
US8590562B2 (en) 2010-12-17 2013-11-26 Lincoln Industries Corporation Fluid flow detection device
US9086186B2 (en) 2011-10-14 2015-07-21 Lincoln Industrial Corporation System having removable lubricant reservoir and lubricant refilling station
US9388941B2 (en) 2011-10-17 2016-07-12 Lincoln Industrial Corporation Compact lubricant injector and injector system
ITMI20120288A1 (it) * 2012-02-27 2013-08-28 Dropsa Spa Dispositivo di lubrificazione con misuratore di portata
US8978825B2 (en) 2012-04-19 2015-03-17 Lincoln Industrial Corporation Dual-line pump unit, lubrication system, and related apparatus and method
DE102012220297A1 (de) * 2012-11-08 2014-05-08 Lincoln Gmbh Schmiervorrichtung
KR101287069B1 (ko) * 2013-05-02 2013-07-17 김민호 원단공급기용 오일공급유닛
CN103256363B (zh) * 2013-05-30 2015-06-17 东北大学 一种单向单步传动机构
US9671065B2 (en) 2013-10-17 2017-06-06 Lincoln Industrial Corporation Pump having wear and wear rate detection
CN106164351B (zh) * 2013-12-20 2019-03-05 美名格－艾罗有限公司 用于针织机的直接喷射润滑系统
US11031772B2 (en) * 2017-04-11 2021-06-08 Hove A/S Protection earth connection detector
DE112018002899B4 (de) * 2017-06-09 2022-09-01 Denso Corporation Elektrische Pumpenvorrichtung
CN110578204A (zh) * 2018-06-07 2019-12-17 广东南豆科技有限公司 一种针织机针道润滑机构
CN109681759A (zh) * 2019-02-25 2019-04-26 山西日盛达新能源集团有限公司 一种防堵塞的压延机轴瓦自动润滑装置
US11435028B2 (en) 2019-04-30 2022-09-06 Lincoln Industrial Corporation Lubricant injector
CN110307465B (zh) * 2019-07-30 2024-01-26 王定根 一种顺序供油装置及挖掘机全自动润滑剂注入装置

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FR1450316A (fr) * 1964-10-20 1966-05-06 Allis Chalmers Mfg Co Pompe d'injection de carburant
CS170564B1 (sk) * 1975-01-14 1976-09-15
JPS57181935A (en) * 1981-05-06 1982-11-09 Diesel Kiki Co Ltd Fuel injection device
US4412519A (en) * 1982-09-13 1983-11-01 General Motors Corporation Diesel fuel distributor type injection pump
CH667702A5 (de) * 1984-02-15 1988-10-31 Barmag Barmer Maschf Zahnradpumpe.
US4528965A (en) * 1984-03-27 1985-07-16 Caterpillar Tractor Co. Rotor balancing for distribution valve
US4632648A (en) * 1985-06-24 1986-12-30 Goyne Thomas S Grease pumps
US4944367A (en) * 1988-12-13 1990-07-31 Watts Fluidair Div. Of Robertshaw Controls Company Injection lubricator with plural outlets
JPH0388957A (ja) * 1989-08-22 1991-04-15 New Zealand Government 圧縮点火エンジンの燃料供給装置及びその制御装置
DE4021557C2 (de) * 1990-07-06 2000-08-17 Sipra Patent Beteiligung Vorrichtung zur Überwachung des Durchflusses eines fließfähigen Mediums durch einen Strömungsraum
DE4104793A1 (de) * 1991-02-16 1992-08-20 Memminger Iro Gmbh Schmiereinrichtung zur versorgung mehrerer schmierstellen, insbesondere einer strickmaschine, mit schmiermittel, vorzugsweise oel
EP0639696B1 (en) * 1993-04-02 1998-01-21 Yamaha Hatsudoki Kabushiki Kaisha Method and system for lubricating an internal combustion engine

Also Published As

Publication number Publication date
TR200000298A2 (tr) 2000-09-21
EP1026300A2 (de) 2000-08-09
USRE40898E1 (en) 2009-09-01
CN1264007A (zh) 2000-08-23
DE50011936D1 (de) 2006-02-02
EP1026300A3 (de) 2001-04-11
JP2000230695A (ja) 2000-08-22
TR200000298A3 (tr) 2000-09-21
UA59404C2 (uk) 2003-09-15
MY123504A (en) 2006-05-31
CA2298296A1 (en) 2000-08-05
CA2298296C (en) 2005-05-10
SK284957B6 (sk) 2006-03-02
DE19904647A1 (de) 2000-08-31
ES2255900T3 (es) 2006-07-16
ATE314513T1 (de) 2006-01-15
SK1192000A3 (en) 2000-11-07
KR100371978B1 (ko) 2003-02-14
ID24778A (id) 2000-08-10
CN1188597C (zh) 2005-02-09
CZ2000270A3 (cs) 2001-04-11
CO5231265A1 (es) 2002-12-27
JP3842000B2 (ja) 2006-11-08
BR0000306A (pt) 2000-10-17
CZ294191B6 (cs) 2004-10-13
TW473603B (en) 2002-01-21
US6322336B1 (en) 2001-11-27
PL338066A1 (en) 2000-08-14
HK1030040A1 (en) 2001-04-20
KR20010006603A (ko) 2001-01-26
PE20010158A1 (es) 2001-02-28
RU2185566C2 (ru) 2002-07-20

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